High energy impact machine



Sept. 8, 1970 J. P. KUZKO ETAL 3,527,080

, HIGH ENERGY IMPACT MACHINE Filed May 25, 1967 v 2 Sheets-Sheet 1 FIG./ I

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J. P. KUZKO EFAL 2 SIICOtS-Ullht Filed May 25. 1967 F/GZ 0 I Z 0 b United States Patent Oflice 3,527,080 Patented Sept. 8, 1970 3,527,080 HIGH ENERGY IMPACT MACHINE Jury Petrovich Kuzko, Sharikopodshipnikovskaya ul. 2, kv. 112, Moscow, U.S.S.R.; Vladimir Alexandrovich Livanov, Moskovskoi obl., Sovetskaya 34, kv. 38; Lev Nikolaevich Konstantinov, Moskovskoi obl., prosp. Pobedy 38/29, kv. 37; Anatoly Petrovich Chekinov, Moskovslroi obl., prosp. Pobedy 29/38, kv. 46; Semen Davydovich Fainbron, Moskovskoi obl., ul. Gorkogo 33, kv. 37; Alexandr Iosifovich Mazur, Moskovskoi obl., ul. Sovetskaya 34, kv. 28; and Mikhail Ivanovich Surkov, Moskovskoi obl., ul. Kuibysheva 29/28, kv. 7, all of Stupino, U.S.S.R.; Afanasy Ivanovich Nazarov, Leuingradskoe shosse, 1 kvartal, korpus 32, kv. 78; Alexandr Petrovich Monakhov, Leningradsky prosp. 91, kv. 140; Nikolai Nikolaevich Maiorov, Leningradsky prosp. 32, kv. 385; and Boris Antonovich Stopachinsky, Ploschad Vosstania 1, kv. 313, all of Moscow, U.S.S.R.; and Stanislav Vladimirovich Ryndenkov, Moskovskoi obl., ul. Chaikovskogo 10, kv. Gennady Alexeevich Shebeko, Moskovskoi obl., Komsomolskaya ul. 17/16, kv. 1; Arkady Vasilievich Androsov, Moskovskoi obl., prosp. Pobedy 29/38, kv. 59; and Veniamin Georgievich Titov, Moskovskoi obl., ul. Sovetskaya 44, kv. 12, all of Stupino, U.S.S.R.

Filed May 25, 1967, Ser. No. 641,314 Claims priority, application U.S.S.R., May 28, 1966, 1,079,593 Int. Cl. B21j 9/12 US. Cl. 72--453 5 Claims ABSTRACT OF THE DISCLOSURE A high energy impact machine is provided with a vertically movable ram supported in a bed which is also vertically movable, the ram and bed carrying facing dies which come together during a power stroke. A free piston is slidably mounted in the bed belowthe ram and the bed is raised and the ram lowered in a ready posi tion by supplying hydraulic fluid under pressure into the space between the ram and piston and thereafter depressurizing the fluid while holding the bed suspended. The power stroke is obtained by supplying air under pressure between the bottom of the bed and the piston which causes the piston and the ram therewith to move upwardly and the body downwardly.

The present invention relates to impact machines used for deforming metal and, more particularly to forging devices which can operate both as a hammer and a press.

Known in the prior art are impact machines having movable colliding masses used for deforming metals.

A disadvantage of these machines is the employment of a rigid connection between the ram and the piston, which is loaded to the limit and, therefore, is not reliable in operation. Another disadvantage of such machines is the necessity of intricate systems of shock-absorbers, which make the machine more complicated in design and decrease its eiiiciency.

Because of these disadvantages, calibration impacts (impacts delivered at the full power of the equipment, which slightly deform the billet to carry out finish-to-size working) are impossible in the known machines, which strongly impedes forging with strict size allowance.

It is an object of the present invention to eliminate the above mentioned disadvantages of the known machines.

This object may be accomplished by the provision of a press hammer with a. pneumatic-hydraulic drive of movable colliding masses of which one is a body and the other is a ram, wherein the power cylinder is made differential, i.e. chambers of different size one chamber housing the operating ram and the other a free piston separating the hydraulic zone from the pneumatic one.

In order to reliably protect the impact machine from destruction in case of a full-power impact without a billet and to exclude all shock absorbers from the design, thus enabling full-power calibration impacts, it is preferably that the weight of the bed portion subject to inertial extension should not exceed 40 percent of the bed total weight.

In order to insure smooth reduction in collision speeds of the bed and the free piston, as well as the changing of the direction of the piston travel at the end of the power stroke, the skirts of the operating ram and the free piston are provided, at the sides facing one another, with annular projections which move towards one another at the end of the power stroke.

In order to improve the operating conditions of the main packing units in the Zone of a feeder member, the ports used for supplying the gaseous medium to the space under the piston are smaller than the width of each separate packing The following detailed description of an embodiment of the invention is given with reference to the accompanying drawing, wherein:

Fig 1 is a vertical sectional view of the impact machine according to the present invention, in the initial position thereof;

FIG. 2 is a sectional view taken on line II--II of FIG. 1 showing the machine in the impact position; and

FIG. 3 is a sectional view taken on line III-III in FIG. 1.

The impact machine consists of a bed 1 including a power cylinder 2. The bed is secured in guides 3 and 4, and is capable of moving therein a vertical direction.

The power cylinder 2 is diflierential i.e. with upper and lower chambers of different size. In the zone of the smaller diameter there is positioned an operating ram 5 carrying a lower die 6. In the zone of the larger diameter there is placed a free piston 7 separating the hydraulic zone A from the air zone B. A plate 8 of the upper portion of the bed carries an upper die 9 and serves as its support at the moment of the collision of the dies. A bottom 10 of the power cylinder 2 embraces the upper portion of a double passage feeder member 11. One passage 12 is used for feeding liquid to the space A. The other passage 13 serves for supplying air into the zone B. From the passage 13 the air is supplied into the space B through apertures bored in the wall of the member 11 in several rows and forming a belt 14. The diameter of every aperture of the belt 14 is smaller than the width of the separate seal of the sealing unit 15. At the sides facing one another, the skirts of the operating ram 5 and free piston 7 are provided with annular projections 16 and 17 which come together at the end of the power stroke and smoothly decrease the collision speeds of the bed 1 and the free piston 7, as well as change the direction of the piston travel at the end of the stroke. The bottom 10 of the power cylinder 2 is fitted with a return valve 18 mounted therein for by-passing air, in case of an overpressure, from the zone B into the passage 13 and into a drain valve 19 by means of which the zone B has communication with the atmosphere.

The bed 1 is made so that the weight of its portion located below the level of the upper die 9 undergoing extension pressure at the moment of the collision of the dies is less than 40 percent of the total weight of the bed.

Owing to this, the bed 1 of the impact machine serves for prevention of its destruction by inertia forces in case of a full-power impact by the press hammer without a billet interposed between the dies.

This also enables the operation without shock absorbers and consequently, full-power calibration impacts.

The impact machine operates as follows.

Under high pressure a liquid is fed to the space via the passage 12, as a result of which the operating ram together with the lower die 6 rises until it contacts the upper die 9, whereupon the bed 1 moves upwards along the guides 3 and 4, since the effective area of ram 5 Within space A is larger than that of the effective area of piston 7. The upward movement of the bed is limited by elongated bolts 20. In the course of this upward movement, the space B is disconnected from the air passage 13, since ports 21 of the bottom move upwards in relation to the belt 14 of bored apertures made in the stationary feeder member 11.

Then air under a pressure somewhat lower than that of the liquid is supplied, along the passage 13, whereupon the passage 13 remains constantly connected to a source of air (not shown in the drawing). Along a pas sage 22 the air is supplied into the space C. The pressure of the liquid in the space A is released to permit ram 5 to descend under gravity and seat onto a key 23; the pressure release in space A is then halted (without additional pressure applied), whereby a depressurized but solid hydraulic column connection remains in a space A between ram 5 and piston 7. Meanwhile, the bed 1 together with the masses (the plate 8 with the upper die 9) attached thereto is kept in a suspended position by the pressure of the air in the space C. The impact machine is ready for operation.

In order to perform a power stroke, the air is let out of the space C along passage 22. Under the action of gravity, the bed together with the masses attached thereto descends along the guides 3 and 4, and the moment the belt 14 of bored apertures is brought in line with the ports 21, the zone B becomes connected with the passage 13. At this moment, the compressed air from the passage 13, is supplied through the belt 14 and ports 21, to the space B, to urge piston 7 upwardly and bed 1, thus causing downwardly the two systems to accelerate towards each other: the free piston 7, a hydraulic column of fluid between piston 7 and ram 5, the operating ram 5 with the lower die 6 and a billet placed therein moving upwards, on the one hand, and the bed 1, plate 8 and upper die 9 moving downwards, on the other hand. Thus, the acceleration is performed within 90 percent of the bed 1 travel and free piston 7 stroke. At the end of the acceleration, during the last 10 percent of the power stroke, the annular projections 17 and 16 provided on the skirts of the operating ram 5 and free piston 7 are brought in line, thus hampering water drainage from the space D, owing to which fact the pressure of the liquid in this space rises, and the bed 1 together with the masses attached thereto is slightly slowed down as a result of the braking, full stop and change of the movement direction of the free piston 7 which, after the stop, starts moving downwards together with the bed 1.

In the course of the acceleration the operating ram 5 stores some kinetic energy, and after the free piston 7 has changed the direction of its movement, the ram 5 continues moving upwards until the collision of the dies, the kinetic energy being absorbed in the deformation of the billet. In case the impact is performed without a billet the kinetic energy is absorbed as a result of resilient deformation of the dies and power members of the construction. The rebound after the collision is damped by an air cushion in the space B.

With the power stroke completed, liquid under high pressure is supplied into the zone A, and, as it has been described hereinabove, the bed 1 travels upwards, whereas the free piston 7 moves downwards; the air from the space B is forced into the passage 13 through the return valve 18, while the air remaining under the piston 7 is drained into the atmosphere through the draining valve 19.

Then, in order to accomplish the power stroke, the cycle of the afore-described operations is repeated.

The key 23 secured in the bed 1 and entering the recess of the operating ram 5 precludes their mutual sliding and fixes the lower position of the ram in the bed. The pneumodrive may include several air cylinders with different pressures of compressed air, connected to the press hammer through a comon valve chest (not shown in the drawing), which enables the connection of the passage 13 of the feeder member 11 to any of the cylinders. This allows, even in case of a multi-impact deformation of the billet, to selectively preset a desired portion of energy for each of the impacts.

Thus, the present design of impact machine makes it possible to provide, and use in the dies, an operating force with a value exceeding many times the strength of the known machines and limited only by the strength of the dies.

When employing only a hydraulic drive, the machine operates as a press.

What is claimed is:

1. A high energy impact machine comprising a vertically movable bed, a ram slidably mounted within said bed for vertical movement between power and retraction strokes, die means on said ram and bed for applying force during the power stroke to a billet placed in the die means, a freely slidable piston in said bed on the side of the ram opposite the die means, means for supplying a hydraulic pressure fluid between the ram and piston to cause the ram and the bed therewith to be raised, said ram descending in said bed when the hydraulic pressure fluid is depressurized between the ram and piston, means for suspending the bed in its raised position by a pressurized gaseous fluid acting there n, means for supplying a pressurized gaseous fluid between said freely slidable piston and the bed and means for releasing said pressurized gaseous fluid holding the bed suspended to urge the freely slidable piston and the ram therewith to travel upwardly in the pressure stroke while the bed is urged downwardly.

2. A machine according to claim 1, wherein said die means comprises a pair of facing dies, one on said ram and the other on said bed, said bed having a weight below the die secured thereto, which is less than 40% of the total weight of the bed.

3. A machine according to claim 1, wherein said ram and piston include respective skirts facing one another, with annular projections which move towards one another at the end of the power stroke.

4. A machine according to claim 1, wherein said means for supplying pressurized gaseous fluid between the freely slidable piston and the bed comprises a member having ports, said bed including a bottom with a sealing unit which rides on said member past said ports, the latter having an admission section with a linear size which is smaller than the width of the sealing unit.

5. A machine according to claim 1 wherein said ram has a smaller diameter than said free piston.

References Cited UNITED STATES PATENTS 3,135,140 6/1964 Ottestad 72453 3,173,286 3/1965 Dischler 72453 3,205,790 9/1965 Bollar 72--453 3,296,853 1/1967 Beche 72-453 3,352,143 11/1967 Bollar 72--453 CHARLES W. LANHAM, Primary Examiner G. P. CROSBY, Assistant Examiner 

